US4996950A - Double pipes for mixed boilers, to the methods of manufacturing such pipes and to the corresponding boilers - Google Patents

Double pipes for mixed boilers, to the methods of manufacturing such pipes and to the corresponding boilers Download PDF

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Publication number
US4996950A
US4996950A US07/504,859 US50485990A US4996950A US 4996950 A US4996950 A US 4996950A US 50485990 A US50485990 A US 50485990A US 4996950 A US4996950 A US 4996950A
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US
United States
Prior art keywords
partition
borders
longitudinal
intermediate partition
juxtaposed
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/504,859
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English (en)
Inventor
Joseph Le Mer
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Chaffoteaux et Maury SAS
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Chaffoteaux et Maury SAS
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Assigned to CHAFFOTEAUX ET MAURY reassignment CHAFFOTEAUX ET MAURY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: LE MER, JOSEPH
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Publication of US4996950A publication Critical patent/US4996950A/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/48—Water heaters for central heating incorporating heaters for domestic water
    • F24H1/52—Water heaters for central heating incorporating heaters for domestic water incorporating heat exchangers for domestic water
    • F24H1/523—Heat exchangers for sanitary water directly heated by the burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/48—Water heaters for central heating incorporating heaters for domestic water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0316—Assemblies of conduits in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49366—Sheet joined to sheet

Definitions

  • the invention relates to mixed hot water boilers, namely boilers which heat water for supplying both a central heating circuit and a domestic or hot water supply circuit.
  • the invention also relates to the double pipes of said boilers and more particularly their rectilinear segments.
  • the rectilinear segments of the kind in question are formed by two metal tubes welded laterally one against the other.
  • the object of the invention is, among other things, to overcome these drawbacks.
  • the rectilinear segments of the double pipes of the kind in question according to the invention comprising two laterally juxtaposed metal duct sections, are essentially characterized in that one at least of these two sections is defined, on its side the furthest away from the other section, by a metal plate whose two longitudinal borders are curved and are welded against the longitudinal borders of an intermediate metal partition also forming part of the segment considered and in that this intermediate partition has stamped bosses whose tops are in contact with the plate and are fixed thereto.
  • recourse is further had to one and/or other of the following arrangements:
  • the two sections are defined outwardly by plates which are symmetrical with each other with respect to the mean plane of the intermediate partition, then flat,
  • each longitudinal end of the intermediate partition is deformed transversely in the form of an S so as to have two longitudinal half-cups open outwardly, separated from each other by a non deformed bridge of the partition and the bottoms of which are juxtaposed jointingly against the facing plates, and each longitudinal plate end is itself deformed in the middle by a longitudinal outwardly open half-cup whose bottom is juxtaposed jointingly against the bridge of the intermediate partition, which defines two necks whose sections are preferably different, these necks being joined to independent external pipe sections,
  • the curved borders of the plates are oriented perpendicularly to the borders of the intermediate partition to which they are welded and the end edges of the first borders are juxtaposed against the lateral faces of the second borders,
  • the bosses projecting respectively from the two faces of the intermediate partition are formed so that the disturbances which they create in the water streams flowing through the two duct sections forming the same rectilinear segment comprising this partition are different,
  • the intermediate partition is formed by a sheet thicker that the sheets forming the two plates with curved borders welded to this partition.
  • the invention also relates to heat exchangers comprising pipes such as defined above as well as the boilers equipped with such exchangers.
  • the invention comprises certain other arrangements which are preferably used at the same time and which will be more explicitly discussed hereafter.
  • FIG. 1, of these drawings shows in cross section a double pipe segment constructed in accordance with the invention
  • FIG. 2 shows this same segment in a perspective view, with portions cut away
  • FIGS. 3 and 4 show respectively in an exploded perspective view and in an end view a longitudinal end of said segment
  • FIG. 5 shows in a top view a boiler heating element constructed using a double pipe according to the invention
  • FIG. 6 shows in a side view, after removal of a plate, a piece of another double pipe also in accordance with the invention.
  • the double pipe considered comprises a first duct A for the flow of central heating water heated by a mixed boiler, and a second duct B for the flow of domestic hot water heated by said boiler,
  • this double pipe comprises rectilinear segments U (FIG. 5) joined together by curved segments V, with which they form a coil, said rectilinear segments being braced by parallel metal fins Z brazed thereon,
  • the two duct sections A and B forming the double pipe are disposed laterally side by side.
  • one at least of the two sections is defined on its side the furthest away from the other section B by a metal plate 1 whose two longitudinal borders 2, 3 are curved and welded to the longitudinal borders of an intermediate metal partition 4,
  • this intermediate partition 4 has stamped bosses or studs 5 whose tops 6 are in contact with plate 1 and are secured thereto.
  • the two sections A and B are defined externally by partitions which are symmetrical with each other with respect to the mean plane of the intermediate partition 4, then flat.
  • the second section B is therefore defined, on its side the furthest away from partition 4, by a metal plate 7 whose two longitudinal borders 8 and 9 are curved and are welded to partition 4.
  • Bosses 5 are then stamped in the partition 4 so as to project alternately from the two faces of this partition, successively in the direction of the two plates.
  • bosses 5 are in particular aligned in two rows parallel to the longitudinal direction of the pipe.
  • each boss is chosen equal to the inner thickness of sections A and B, reckoned perpendicularly to partition 4 so that, during manufacture of said sections, the tops 6 of these bosses come into contact with the facing plates 1 and 7.
  • Partition 4 may be formed by a metal sheet or strip thicker than that forming the two plates 1 and 7, these thicknesses being for example 1.2 mm for the partition and 0.8 mm for the plates.
  • plates 1 and 7 and partition 4 are formed by strips stamped from the same metal sheet, particularly copper, which simplifies manufacture.
  • the filler metal required for each weld may advantageously be formed by a lateral edge T of said partition 4, which is caused to project slightly with respect to the edges of the curved borders 2, 3, 8, 9 to be welded, as can be seen in FIG. 1.
  • the weld is then made by placing a welding head, shown schematically by the arrow S in FIG. 1, facing said projecting edge T and causing edge T to travel longitudinally in front of the head S or conversely.
  • the molten metal which results from heating the edge is mixed with the molten metal from the curved adjacent borders so as to form, after cooling, a regular and sealed welding bead 10 (FIG. 2).
  • the curves of borders 2, 3, 8, 9 advantageously have a profile in the form of a quarter of a circle so that the edges of these borders are oriented perpendicularly to the mean plane of the partition 4 and are juxtaposed against the lateral marginal faces of the borders of this partition 4.
  • each welded zone After welding, the external face of each welded zone has a smooth and continuous semi-cylindrical shape, as can be clearly seen in FIG. 2.
  • bosses 5 are fixed by brazing against the faces of plates 1 and 7 which are applied thereagainst.
  • each rectilinear segment formed of two sections A and B fastened side by side is in short defined by two parallel flat walls joined together by two curved portions having a semi-circular section: the cross section of this segment can in short be inscribed in an elongate rectangle whose width is generally between 8 and 20 mm, preferably about 10 mm and whose length is generally between 40 and 100 mm, being generally about 60 mm.
  • Bosses 5 are advantageously in the form of rounded nipples whose base is oval and elongate in the longitudinal direction of the pipe, the large axis of the oval being about 8 mm and its small axis about 4 mm and the longitudinal spacing between the successive bosses being about 8 mm.
  • Each longitudinal end of the intermediate partition 4 is deformed transversely in the form of an S so as to have two longitudinally half-cups 11, 12 open longitudinally outwardly and projecting respectively from the two opposite faces of the partition.
  • each half-cup is equal to the thickness of a section A, B so that its bottom is juxtaposed jointingly against the facing plate 1, 7.
  • Each half-cup 11, 12 is separated from the adjacent longitudinal border of partition 4 by a flat narrow and undeformed margin 15, 16 of this partition.
  • each longitudinal end of the plate is deformed so as to form a longitudinal half-cup 14, smaller than the preceding ones, which is also open longitudinally outwardly and whose depth is such that its bottom is juxtaposed jointingly against bridge 13.
  • the wall portions in mutual contact are advantageously brazed together.
  • each neck 17, 18 is formed at each longitudinal end of each rectilinear segment U, each neck serving only one of the two sections A and B of this segment.
  • neck 17 serving only the section A is defined by the half-cup 11 and the facing portion of plate 1, this neck being closed, on the side of the longitudinal border of the segment considered, by welding curved border 2 against margin 15 and, at about the middle of the height of said segment, by application of the bottom of the corresponding half-cup 14 against the facing bridge 13.
  • necks 17 and 18 follows automatically from manufacture of the corresponding rectilinear pipe segment, which is extremely simple since it is sufficient:
  • the numbers of such bosses projecting respectively on each side of partition 4 are given different values, this number being higher for section A in which the central heating water flows than in section B through which the domestic hot water flows.
  • the Applicant has in fact observed that the risk of scaling is higher in the second circuit than in the first since, in the first case, the heating water flows through a closed circuit and therefore carries a proportion of mineral charges which becomes smaller and smaller as its flows.
  • the number of bosses projecting in section A is equal to twice the number of bosses projecting in section B and shown with a thick line.
  • the above necks 17 assigned to the heating circuit are given a larger section than the necks 18 assigned to the domestic hot water circuit.
  • the arrangement proposed provides a saving of metal with respect to those using tubes fixed one against the other and leading to the formation of double walls,

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Branch Pipes, Bends, And The Like (AREA)
US07/504,859 1989-04-07 1990-04-05 Double pipes for mixed boilers, to the methods of manufacturing such pipes and to the corresponding boilers Expired - Fee Related US4996950A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8904609 1988-04-07
FR8904609A FR2645633B1 (fr) 1989-04-07 1989-04-07 Perfectionnements aux tubulures doubles pour chaudieres mixtes, aux procedes de fabrication de ces tubulures et aux chaudieres correspondantes

Publications (1)

Publication Number Publication Date
US4996950A true US4996950A (en) 1991-03-05

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ID=9380499

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/504,859 Expired - Fee Related US4996950A (en) 1989-04-07 1990-04-05 Double pipes for mixed boilers, to the methods of manufacturing such pipes and to the corresponding boilers

Country Status (19)

Country Link
US (1) US4996950A (el)
EP (1) EP0391781B1 (el)
JP (1) JPH02293598A (el)
KR (1) KR900016724A (el)
CN (1) CN1046219A (el)
AT (1) ATE76497T1 (el)
AU (1) AU621734B2 (el)
BR (1) BR9001638A (el)
CA (1) CA2013838A1 (el)
DE (1) DE69000108D1 (el)
DK (1) DK0391781T3 (el)
ES (1) ES2031403T3 (el)
FR (1) FR2645633B1 (el)
GR (1) GR3004676T3 (el)
MA (1) MA21801A1 (el)
PT (1) PT93682A (el)
TN (1) TNSN90048A1 (el)
TR (1) TR25998A (el)
ZA (1) ZA902551B (el)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5156327A (en) * 1990-04-03 1992-10-20 Mitsubishi Jukogyo Kabushiki Kaisha Procedure for molding composite materials
US5604981A (en) * 1995-04-06 1997-02-25 Ford Motor Company Method of making an automotive evaporator
SG81243A1 (en) * 1998-08-20 2001-06-19 Pressed Metal Ind Pte Ltd A method of manufacturing a barrier
US20020028318A1 (en) * 1996-09-13 2002-03-07 Clark Brian Hall Structural dimple panel
US20070204980A1 (en) * 2004-10-13 2007-09-06 Kyungdong Boiler Co., Ltd. Heat Exchanger for Common Use for Boiler and Hot Water Supply
US20080006397A1 (en) * 2004-11-25 2008-01-10 Masaaki Kitazawa Heat Exchanger
US20090133861A1 (en) * 2005-12-14 2009-05-28 Kyungdong Navien Co., Ltd. Heat Exchanger of Condensing Boiler for Heating and Hot-Water Supply
DE102011013244A1 (de) * 2011-03-07 2012-09-13 Arup Alu-Rohr Und Profil Gmbh Turbulenzeinlage für flache Wärmetauscherrohre, Flachrohr für einen Wärmetauscher mit einer derartigen Turbulenzeinlage, Wärmetauscher mit derartigen Flachrohren, sowie Verfahren und Vorrichtung zur Herstellung eines derartigen Flachrohres
US11692727B2 (en) * 2017-02-07 2023-07-04 Uniflair S.P.A. Cooling system with reduced pressure drop

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010006277A1 (de) * 2010-01-25 2011-07-28 Joma-Polytec GmbH, 72411 Wärmetauscher, insbesondere zur Vorwärmung von Verbrennungsluft von Warmwasserheizkesseln
CN102538537A (zh) * 2012-02-04 2012-07-04 佛山市太阳花散热器有限公司 采暖散热器的散热管及其加工方法
CN108801029B (zh) * 2018-07-09 2019-12-03 安徽硅宝有机硅新材料有限公司 一种化工生产用热交换器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1823919A (en) * 1929-03-28 1931-09-22 Frigidaire Corp Refrigerating apparatus
GB994946A (en) * 1962-05-26 1965-06-10 Marcel Leblanc An improved central heating installation with hot water circuit for domestic use
EP0022025A2 (fr) * 1979-06-25 1981-01-07 Chaffoteaux & Maury Echangeur de chaleur à double enveloppe
US4655174A (en) * 1979-04-26 1987-04-07 Fillios Jean P R Hot liquid generator with condensation and installation incorporating this generator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH398657A (de) * 1962-05-11 1966-03-15 Sulzer Ag Rohr für Wärmeübertrager
CH433653A (de) * 1964-11-19 1967-04-15 Runtaltherm Ag Verfahren zur wahlweisen Erwärmung von Flüssigkeiten sowie Einrichtung zur Durchführung dieses Verfahrens
DE1274310B (de) * 1966-07-01 1968-08-01 Runtaltherm A G Umlauferhitzer mit Brauchwasserbereitung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1823919A (en) * 1929-03-28 1931-09-22 Frigidaire Corp Refrigerating apparatus
GB994946A (en) * 1962-05-26 1965-06-10 Marcel Leblanc An improved central heating installation with hot water circuit for domestic use
US4655174A (en) * 1979-04-26 1987-04-07 Fillios Jean P R Hot liquid generator with condensation and installation incorporating this generator
EP0022025A2 (fr) * 1979-06-25 1981-01-07 Chaffoteaux & Maury Echangeur de chaleur à double enveloppe

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5156327A (en) * 1990-04-03 1992-10-20 Mitsubishi Jukogyo Kabushiki Kaisha Procedure for molding composite materials
US5604981A (en) * 1995-04-06 1997-02-25 Ford Motor Company Method of making an automotive evaporator
US20020028318A1 (en) * 1996-09-13 2002-03-07 Clark Brian Hall Structural dimple panel
US6939599B2 (en) * 1996-09-13 2005-09-06 Brian H. Clark Structural dimple panel
SG81243A1 (en) * 1998-08-20 2001-06-19 Pressed Metal Ind Pte Ltd A method of manufacturing a barrier
US20070204980A1 (en) * 2004-10-13 2007-09-06 Kyungdong Boiler Co., Ltd. Heat Exchanger for Common Use for Boiler and Hot Water Supply
US20080006397A1 (en) * 2004-11-25 2008-01-10 Masaaki Kitazawa Heat Exchanger
US9086245B2 (en) * 2004-11-25 2015-07-21 Daikin Industries, Ltd. Heat exchanger
US20090133861A1 (en) * 2005-12-14 2009-05-28 Kyungdong Navien Co., Ltd. Heat Exchanger of Condensing Boiler for Heating and Hot-Water Supply
US8220529B2 (en) * 2005-12-14 2012-07-17 Kyungdong Navien Co., Ltd. Heat exchanger of condensing boiler for heating and hot-water supply
DE102011013244A1 (de) * 2011-03-07 2012-09-13 Arup Alu-Rohr Und Profil Gmbh Turbulenzeinlage für flache Wärmetauscherrohre, Flachrohr für einen Wärmetauscher mit einer derartigen Turbulenzeinlage, Wärmetauscher mit derartigen Flachrohren, sowie Verfahren und Vorrichtung zur Herstellung eines derartigen Flachrohres
WO2012119660A2 (de) * 2011-03-07 2012-09-13 Arup Alu-Rohr Und Profil Gmbh Turbulenzeinlage für flache wärmetauscherrohre; flachrohr für einen wärmetauscher mit einer derartigen turbulenzeinlage, wärmetauscher mit derartigen flachrohren, sowie verfahren und vorrichtung zur herstellung eines derartigen flachrohres
WO2012119660A3 (de) * 2011-03-07 2012-11-15 Arup Alu-Rohr Und Profil Gmbh Turbulenzeinlage für flache wärmetauscherrohre; flachrohr für einen wärmetauscher mit einer derartigen turbulenzeinlage, wärmetauscher mit derartigen flachrohren, sowie verfahren und vorrichtung zur herstellung eines derartigen flachrohres
US11692727B2 (en) * 2017-02-07 2023-07-04 Uniflair S.P.A. Cooling system with reduced pressure drop

Also Published As

Publication number Publication date
AU5300990A (en) 1990-10-11
DK0391781T3 (da) 1992-07-13
ZA902551B (en) 1991-06-26
MA21801A1 (fr) 1990-12-31
BR9001638A (pt) 1991-05-07
CN1046219A (zh) 1990-10-17
PT93682A (pt) 1991-12-31
TNSN90048A1 (fr) 1991-03-05
EP0391781B1 (fr) 1992-05-20
ES2031403T3 (es) 1992-12-01
TR25998A (tr) 1993-11-01
CA2013838A1 (en) 1990-10-07
GR3004676T3 (el) 1993-04-28
JPH02293598A (ja) 1990-12-04
DE69000108D1 (de) 1992-06-25
EP0391781A1 (fr) 1990-10-10
ATE76497T1 (de) 1992-06-15
FR2645633A1 (fr) 1990-10-12
AU621734B2 (en) 1992-03-19
FR2645633B1 (fr) 1991-07-12
KR900016724A (ko) 1990-11-14

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